Condensation reduction device for an EGR equipped system

ABSTRACT

A condensation reduction device for use with an engine is disclosed. The condensation reduction device may have a first body member configured to receive a flow of exhaust, and a reservoir in fluid communication with the first body member to collect condensate from the flow of exhaust. The condensation reduction device may further have a passageway in fluid communication with the reservoir to direct the collected condensate from the reservoir back into the flow of exhaust.

TECHNICAL FIELD

The present disclosure relates generally to an EGR equipped combustionsystem and, more particularly, to an EGR equipped combustion systemhaving a condensation reduction device.

BACKGROUND

Internal combustion engines exhaust a complex mixture of air pollutants.These air pollutants are composed of solid particulate matter andgaseous compounds including nitrogen oxides (NOx). Due to increasedattention on the environment, exhaust emission standards have becomemore stringent and the amount of solid particulate matter and gaseouscompounds emitted to the atmosphere from an engine is regulateddepending on the type of engine, size of engine, and/or class of engine.

One method that has been implemented by engine manufacturers to complywith the regulation of these engine emissions is exhaust gasrecirculation (EGR). EGR systems recirculate exhaust gas by-productsinto the intake of an internal combustion engine. The exhaust gas, whichis redirected to a cylinder of the engine, reduces the concentration ofoxygen therein, thereby lowering the maximum combustion temperaturewithin the cylinder. The lowered maximum combustion temperature slowsthe chemical reaction of the combustion process, thereby decreasing theformation of nitrogen oxides. In addition, some of the particulatematter entrained in the exhaust is burned upon reintroduction into theengine cylinder to further reduce the exhaust gas by-products.

Before the exhaust gas enters the engine cylinders, it must first bemixed with air and cooled to the proper temperature. To cool the mixtureof air and exhaust, the mixture is directed through a heat exchanger.While in the heat exchanger and at locations downstream of the heatexchanger, moisture previously entrained in the air and exhaust mixturecondenses on the relatively cool walls of the heat exchanger. Because ofthe presence of sulfur and nitrogen oxides in the exhaust, thecondensate can be corrosive and potentially damaging to the heatexchanger, downstream passageways, and the engine. The condensate mayalso cause premature wear of the engine due to the condensate'smechanical interactions with the piston, piston rings, and engine valvesas the pistons reciprocate and the valves open within the cylinders.

One way to minimize the damage caused by condensation is disclosed inU.S. Pat. No. 6,748,741 (the '741 patent) issued to Martin et al. onJun. 15, 2004. Specifically, the '741 patent discloses a charge aircondensation separation system for a turbocharged engine employing EGR.The separation system includes a turbocharger having a compressorproviding charge air, with a charge air cooler connected to thecompressor to cool the charge air. A charge air delivery duct isconnected to an outlet of the charge air cooler, and a toroidal traphaving an annular inlet is disposed in the charge air delivery duct. Aswirl generator may be used to urge the condensate toward the walls ofthe charge air duct for subsequent trapping. The toroidal trap has asump for collecting condensation internal to the toroidal trap. A drainline for removing condensation from the sump for expulsion to theatmosphere is connected to the trap, and a pump or other device forovercoming a pressure differential in the drain line is employed incertain embodiments.

Although the separation system of the '741 patent may help to minimizedamage resulting from condensation-caused acid, it may be limited andresult in poor engine emissions. Specifically, although condensate fromthe charge air may be removed from the system, condensate from therecirculated exhaust may be unrestricted. That is, moisture from therecirculated exhaust flow may still be allowed to condense within theduct work of the engine and, because the separation system only removescondensate from the charge air, the condensed liquid from therecirculated exhaust flow may travel unrestricted into and damage theengine. And, because the acid solution is mainly caused by sulfurcompounds and nitrogen oxides in the recirculated exhaust flow, thecondensate from the exhaust may be more damaging than the condensatefrom the charge air. Further, it has been shown that the introduction ofwell dispersed or atomized (i.e., not condensed) non-combustible fluidinto the combustion chamber of an engine during operation may be helpfulin reducing the amount of NOx produced by the engine. Thus, because theseparation system of the '741 patent removes the fluid from the chargeair flow rather than homogeneously redispersing it into the air flow,the NOx production of the engine may be excessive.

The disclosed condensation reduction device is directed to overcomingone or more of the problems set forth above.

SUMMARY OF THE DISCLOSURE

In one aspect, the present disclosure is directed to a condensationreduction device. The condensation reduction device may include a firstbody member configured to receive a flow of exhaust, and a reservoir influid communication with the first body member to collect condensatefrom the flow of exhaust. The condensation reduction device may furtherinclude a passageway in fluid communication with the reservoir to directthe collected condensate from the reservoir back into the flow ofexhaust.

In another aspect, the present disclosure is directed to a method ofre-dispersing condensate. The method may include generating a flow ofexhaust, and mixing the flow of exhaust with air. The method may alsoinclude cooling the mixed flow of air and exhaust, and collectingcondensate from the cooled and mixed flow of air and exhaust. The methodmay further include directing the collected condensate back into thecooled and mixed flow of air and exhaust prior to combustion of thecooled and mixed flow of air and exhaust.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagrammatic illustration of an exemplary disclosed fluidhandling system; and

FIG. 2 is a cross sectional illustration of an exemplary disclosedcondensation reduction device for use with the fluid handling system ofFIG. 1.

FIG. 3 is a cross sectional illustration of another exemplary disclosedcondensation reduction device for use with the fluid handling system ofFIG. 1

DETAILED DESCRIPTION

FIG. 1 illustrates an exemplary fluid handling system 12 for use with apower source 10. Power source 10 may include an engine, such as, forexample, a diesel engine, a gasoline engine, a gaseous fuel-poweredengine, such as a natural gas engine, or any other type of combustionengine apparent to one skilled in the art. It is also considered thatpower source 10 may alternatively include a furnace or similarnon-engine device. Fluid handling system 12 may direct air into andexhaust away from power source 10, and may include an exhaust system 16,an EGR system 18, and an air induction system 14.

Exhaust system 16 may include a means for directing exhaust flow out ofpower source 10. For example, exhaust system 16 may include one or moreturbines 32 fluidly communicated in a series relationship. Each turbine32 may be connected to drive one or more compressors 24 of air inductionsystem 14. In particular, as the hot exhaust gases exiting power source10 expand against blades (not shown) of turbine 32, turbine 32 mayrotate and drive the connected compressor 24. It is contemplated thatturbines 32 may alternatively be disposed in a parallel relationship orthat only a single turbine 32 may be included within exhaust system 16.It is also contemplated that turbines 32 may be omitted, if desired, andcompressors 24 driven by power source 10 mechanically, hydraulically,electrically, or in any other manner known in the art.

EGR system 18 may include a means for redirecting a portion of theexhaust flow from exhaust system 16 into air induction system 14. Forexample, EGR system 18 may include an inlet port 40, a recirculationparticulate filter 42, an exhaust cooler 44, a recirculation valve 46,and a discharge port 48. It is contemplated that EGR system 18 mayinclude additional or different components, such as a catalyst, anelectrostatic precipitation device, a shield gas system, one or moresensing elements, and/or other means for redirecting that are known inthe art.

Inlet port 40 may be connected to exhaust system 16 to receive at leasta portion of the exhaust flow from power source 10. Specifically, inletport 40 may be disposed downstream of turbines 32 to receive lowpressure exhaust gases from exhaust passageway 49. It is contemplatedthat inlet port 40 may alternatively be located upstream of turbines 32for a high pressure recirculation application, if desired.

Recirculation particulate filter 42 may be connected to inlet port 40via a fluid passageway 50 to remove particulates from the portion of theexhaust flow directed through inlet port 40. Recirculation particulatefilter 42 may include electrically conductive or non-conductive coarsemesh elements. It is contemplated that recirculation particulate filter42 may include a catalyst for reducing an ignition temperature of theparticulate matter trapped by recirculation particulate filter 42, ameans for regenerating the particulate matter trapped by recirculationparticulate filter 42, or both a catalyst and a means for regenerating.The means for regenerating may include, among other things, afuel-powered burner, an electrically-resistive heater, an engine controlstrategy, or any other means for regenerating known in the art. It iscontemplated that recirculation particulate filter 42 may be omitted, ifdesired.

Exhaust cooler 44 may be fluidly connected to recirculation particulatefilter 42 via a fluid passageway 52 to cool the portion of exhaust gasesflowing through inlet port 40. Exhaust cooler 44 may include aliquid-to-air heat exchanger, an air-to-air heat exchanger, or any othertype of heat exchanger known in the art for cooling an exhaust flow. Itis contemplated that exhaust cooler 44 may be omitted, if desired.

Recirculation valve 46 may be fluidly connected to exhaust cooler 44 viaa fluid passageway 54 to regulate the flow of cooled exhaust enteringair induction system 14. Recirculation valve 46 may embody a butterflyvalve, a gate valve, a ball valve, a globe valve, or any other valveknown in the art. Recirculation valve 46 may be solenoid-actuated,hydraulically-actuated, pneumatically-actuated, or actuated in any othermanner.

Air induction system 14 may include a means for introducing cooled andcompressed air or an air and exhaust mixture into a combustion chamber20 of power source 10. For example, air induction system 14 may includean induction valve 22, compressors 24, an air cooler 26, a condensationreduction device 27, and an intake manifold 25. It is contemplated thatadditional components may be included within air induction system 14,such as, for example, additional valving, one or more air cleaners, oneor more waste gates, a control system, and other means for introducingcharge air into combustion chambers 20 that are known in the art.

Induction valve 22 may be fluidly connected to compressors 24 via afluid passageway 28 to regulate the flow of atmospheric air to powersource 10. As atmospheric air enters induction valve 22, it may mix withthe exhaust exiting discharge port 48, creating an air and exhaustmixture. Induction valve 22 may embody a butterfly valve, a gate valve,a ball valve, a globe valve, or any other type of valve known in theart. Induction valve 22 may be solenoid-actuated,hydraulically-actuated, pneumatically-actuated, or actuated in any othermanner. It is contemplated that induction valve 22 and recirculationvalve 46 may be combined into a single integral valve that performs theair and exhaust regulating and mixing functions, if desired.

Compressors 24 may compress the air and exhaust (or just air whenrecirculation valve 46 is closed) flowing into power source 10 to apredetermined pressure level. Each of compressors 24 may include a fixedgeometry compressor, a variable geometry compressor, or any other typeof compressor known in the art. Compressors 24 may be fluidly connectedto air cooler 26 via fluid passageway 30 and may be disposed in a seriesrelationship. It is contemplated that compressors 24 may alternativelybe disposed in a parallel relationship or that air induction system 14may include only a single compressor 24. It is further contemplated thatcompressors 24 may be omitted, when a non-pressurized induction systemis desired.

Air cooler 26 may embody an air-to-air heat exchanger or anair-to-liquid heat exchanger and may facilitate the transfer of thermalenergy to or from the air and exhaust mixture directed into power source10. For example, air cooler 26 may include a shell and tube-type heatexchanger, a corrugated plate-type heat exchanger, a tube and fin-typeheat exchanger, a bar-and-plate type heat exchanger, or any other typeof heat exchanger known in the art. Air cooler 26 may be connected tocondensation reduction device 27 via fluid passageway 31. It iscontemplated that air cooler 26 may alternatively be located upstream ofcompressors 24, and/or that air induction system 14 may include two ormore coolers located upstream and/or downstream of compressors 24.

As shown in FIG. 2, condensation reduction device 27 may include a meansfor atomizing and re-entraining condensed vapor (e.g., condensed water,sulfuric acid, nitric acid, etc.) into the charge air or air and exhaustflow before the fluid enters intake manifold 25 via fluid passageway 33(see FIG. 1). Condensation reduction device 27 may include a first body56, a second body 58, an annular reservoir 62, a passageway 60, and aheater 64.

First body 56 may be a hollow tubular member configured to receive andconduct a fluid (e.g., air, exhaust gas, or a mixture of air andexhaust) from passageway 31 to second body 58. First body 56 may includean inlet 66 configured to receive the air and exhaust gas mixture, anexpanded section 70, and a coupling section 68. First body 56 may bemanufactured from any appropriate material having anti-corrosioncharacteristics, such as, for example, stainless steel, aluminum,plastic, composite, or any other material known in the art. First body56 may be machined, cast, molded, or formed in any other appropriatemanner.

An inner diameter of first body 56 may increase at expanded section 70relative to inlet 66 (i.e., inner diameter increases in the direction offluid flow). Expanded section 70 may allow second body 58 to be receivedwithin first body 56. Expanded section 70 may be located at any axiallocation between inlet 66 and coupling section 68 of first body 56. Theincrease in inner diameter at expanded section 70 may be immediate(e.g., a step increase in diameter) or it may be gradual (e.g., agenerally linear increase in diameter with respect to a central axis61). A gradual increase in the inner diameter of first body 56 may helpto prevent flow separation at expanded section 70, thus minimizingpressure loss.

Coupling section 68 of first body 56 may interface and/or connect withsecond body 58. For example, coupling section 68 may connect with secondbody 58 via a fastening member, such as, for example, a bolt, a screw, adowel pin, or any other appropriate fastening member. It is alsocontemplated that coupling section 68 may be internally threaded, ifdesired.

Second body 58 may be located downstream of and in fluid communicationwith first body 56. Second body 58 may also be a hollow tubular memberconfigured to receive and conduct a fluid (e.g., air, exhaust gas, ormixture of air and exhaust) from first body 56 to fluid passageway 33.Second body 58 may include an inlet 71, a coupling section 72, a throatsection 74, an expanded section 76, and an outlet 78. Second body 58 maybe manufactured from a corrosion resistant material, such as, forexample, stainless steel, aluminum, plastic, composite, or any othermaterial known or used in the art. Second body 58 may be machined, cast,molded, or formed in any other appropriate manner.

Coupling section 72 may interface and/or connect with coupling section68 of first body 56. An outer diameter of second body 58 at couplingsection 68 may be slightly smaller than the inner diameter of first body56 at coupling section 72, such that the smaller diameter second body 58may be axially received within the larger diameter of first body 56. Itis contemplated that fastening members (not shown) may be used to joinfirst and second bodies 56 and 58. It is also contemplated that couplingsection 72 may be externally threaded such that it may be received bycorresponding internal threads of coupling section 68. Coupling section72 may alternatively be joined to coupling section 68 via welding,brazing, chemical bonding, or in any other manner known or used in theart. In another embodiment shown in FIG. 3, it is contemplated thatcoupling sections 68 and 72 may be omitted and first body 56 and secondbody 58 may be cast, injection molded or otherwise formed as a singleintegral part, if desired.

Referring to FIG. 2, A sealing member 73 may be located between couplingsections 68 and 72 to restrict the flow of air, exhaust gas, and/orcondensate. Sealing member 73 may be an o-ring, a gasket, an adhesivesubstance, or any other appropriate sealing member known in the art. Itis contemplated that multiple sealing members 73 may be used to restrictthe flow of exhaust gas, air and/or condensate, if desired.

Throat section 74 may be a section of reduced internal diameter (i.e., aconstriction), as compared to the internal diameter of first body 56immediately upstream of expanded section 70. This reduced diametersection of second body 58 may cause a pressure decrease and a velocityincrease of the air and exhaust mixture at throat section 74 relative toan upstream pressure and velocity. This decrease in pressure andincrease in velocity of the air and exhaust mixture may provide apotential for enhanced mixing of fluid particles introduced from annularreservoir 62 into the mixture at throat section 74. It is contemplatedthat the reduction in the diameter of throat section 74 may be optimizedto achieve a desired fluid pressure and velocity at throat section 74.It is also contemplated that, instead of modifying the internal diameterof second body 58 at throat section 74, a separate venturi tube ororifice plate may be located within the flow path to achieve a similarresult, if desired.

Expanded section 76 may be a section where the internal diameter ofsecond body 58 is increased relative to the internal diameter of secondbody 58 at throat section 74. The internal diameter at expanded section76 may increase at a relatively constant angle, α, along the axiallength of expanded section 76. The increase in diameter of second body58 at expanded section 76 may decrease the velocity and increase thepressure of the air and exhaust gas mixture. The angle α may be selectedto avoid significant flow separation along expanded section 76(separation may occur with a large value of α), yet still achieve acompact design of condensation reduction device 27 (compact design maybe difficult with a small value of α). In one embodiment, a may beapproximately 6 degrees. It is contemplated that the internal diameterof second body 58 at expanded section 76 may increase at a non-constantrate, if desired.

Both outlet 78 of second body 58 and inlet 66 of first body 56 mayinclude a connecting element 96 for connecting condensation reductiondevice 27 to fluid passageways 33 and 31 of fluid handling system 12(see FIG. 1), respectively. For example, connecting element 96 mayembody an annular channel or notch in an outer surface of first body 56.Passageway 31 may be received by connecting element 96, and an annularband (not shown) may be tightened around an outer diameter of passageway31 at the channeled location. The band may be tightened until passageway31 deforms into the channel, thus securing passageway 31 in place.Passageway 33 may be secured to second body 58 in a similar fashion. Itis contemplated that each connecting element 96 may alternatively embodya threaded connection, a flanged connection, or any other type ofmechanical connection known in the art. It is further contemplated thata welded connection, an interference connection, a brazed connection, orany other appropriate connection may be used in place of connectingelement 96, if desired.

Annular reservoir 62 may be situated to collect condensate flowing alongan internal surface 80 of first body 56. A geometry of annular reservoir62 may be at least partially defined by an external surface 82 of secondbody 58 and internal surface 80 of first body 56 at or near throatsection 74. It is contemplated that annular reservoir 62 mayalternatively be an annular trough or channel in internal surface 80 offirst body 56 located at or upstream of throat section 74.

Passageway 60 may introduce or reintroduce condensate from annularreservoir 62 into the fluid stream passing through condensationreduction device 27. Passageway 60 may include an inlet 84 to receivecondensate collected by annular reservoir 62. Because gravity may causethe condensate to pool at a bottom location of annular reservoir 62,inlet 84 may be located at or near the bottom (i.e., gravitationallylowest point) of annular reservoir 62. Passageway 60 may also include anoutlet 86 to allow the condensate received via inlet 84 to be drawn bythe low pressure at throat 74 into the flow of fluid. Passageway 60 mayembody a hose, a duct, a pipe, or any other fluid carrying member knownin the art. It is contemplated that passageway 60 may be routed in anyappropriate pathway that commences at or near the bottom of annularreservoir 62 and terminates at throat section 74 of second body 58. Forexample, passageway 60 may be located in a wall of second body 58 at ornear throat section 74 and may extend generally toward central axis 61of second body 58. It is also contemplated that multiple passageways 60may be used, if desired.

When the condensate is reintroduced into the flow of air and exhaust,heat from the air and exhaust gas mixture may help atomize thecondensate. If needed, additional heat may be provided by heater 64.Heater 64 may be used to transmit thermal energy into the condensatecollected within annular reservoir 62. Heater 64 may include a housing88 defining an inlet port 90, an annular cavity 94, and a outlet port92. Housing 88 may attach to first body 56 via mechanical fastening,welding, brazing, chemical bonding, or in any other appropriate manner.A heated fluid may pass into annular cavity 94 of housing 88 via inletport 90. The heated fluid may then travel around annular cavity 94 andexit via outlet port 92. Thermal energy from the heated fluid may beconducted through first body 56 and transferred to the lower temperaturecondensate contained within annular reservoir 62, thus increasing thecondensate's ability to atomize. Multiple inlet and outlet ports 90 and92 may be used, if desired. It is contemplated that any readilyavailable fluid may be used for heating, such as, for example, heatedengine oil, heated coolant, heated air, or any other appropriate fluid.It is also contemplated that heater 64 may alternatively embody anelectrical heater, a gas heater, or may be omitted, if desired.

INDUSTRIAL APPLICABILITY

The disclosed fluid handling system may be applicable to any combustiondevice, such as an engine or a furnace, where mechanical and/orcorrosive damage from condensate is a concern. The disclosed fluidhandling system may atomize and re-entrain collected condensate into aflow of air and/or exhaust before the condensate enters the combustiondevice. The disclosed fluid handling system may provide a simple andinexpensive means for simultaneously decreasing system degradation andimproving the engine's emission characteristics. Operation of thedisclosed fluid handling system will now be described.

Referring to FIG. 1, atmospheric air may be drawn into air inductionsystem 14 via induction valve 22 to compressors 24, where it may bepressurized to a predetermined level before entering combustion chambers20 of power source 10. Fuel may be mixed with the pressurized air beforeor after entering combustion chambers 20. This fuel-air mixture may thenbe combusted by power source 10 to produce mechanical work and anexhaust flow containing gaseous compounds and solid particulate matter.The exhaust flow may be directed from power source 10 to turbines 32where the expansion of hot exhaust gases may cause turbines 32 torotate, thereby rotating connected compressors 24 to compress the inletair. After exiting turbines 32, the exhaust flow may be divided into twoflows, including a first flow redirected back to air induction system 14and a second flow directed to the atmosphere.

As the first exhaust flow moves through inlet port 40 of EGR system 18,it may be filtered by recirculation particulate filter 42 to removeparticulate matter prior to communication with exhaust cooler 44. Theparticulate matter, when deposited on the mesh elements of recirculationparticulate filter 42, may be passively and/or actively regenerated. Itis contemplated that the particulate matter may additionally oralternatively be filtered prior to entering inlet port 40, if desired.

The flow of the reduced-particulate exhaust from recirculationparticulate filter 42 may be cooled by exhaust cooler 44 and thendirected through recirculation valve 46 to be drawn back into airinduction system 14 by compressors 24. The recirculated exhaust flow maybe mixed with the air entering combustion chambers 20. The exhaust,which is directed to combustion chambers 20, may reduce theconcentration of oxygen therein and, in turn, lower the maximumcombustion temperature within power source 10. The lowered maximumcombustion temperature may slow the chemical reaction of the combustionprocess, thereby decreasing the formation of nitrogen oxides. In thismanner, the gaseous pollution produced by power source 10 may bereduced. The lower peak combustion temperature may also result inimproved efficiency of power source 10 by reducing heat rejection andchemical dissociation.

Prior to entering power source 10, the mixture of air and exhaust may becooled using exhaust cooler 44 and/or air cooler 26 so as to improve thelongevity, performance, and emission characteristics of power source 10.As the mixture of inlet air and recirculated exhaust gases flows throughair cooler 26, and the other passageways of air induction system 14,heat may be transferred from the higher temperature air and exhaustmixture to the lower temperature walls and/or cooling fluid. Because thevapor pressure of the air and exhaust mixture may decrease withdecreasing temperature, vapor from the cooling mixture may condense andbegin to flow along the passageways of air induction system 14. Thiscondensate may form corrosive substances. For example, sulfur dioxideand trioxide (SO2 and SO3) and nitrogen oxides (NOx) in the exhaust mayreact with condensed water vapor and form sulfuric and nitric acid. Theacidic condensate may eventually corrode portions of air inductionsystem 14 and power source 10. The liquid condensate may also causemechanical damage and enhanced wear when it reaches power source 10 andinteracts with the power source's moving parts. However, a finelydispersed vapor or aerosol may cool the combustion process within powersource 10 and thereby help to reduce the amount of NOx produced by powersource 10.

Condensation reduction device 27 may atomize and re-entrain condensedliquid into the air and exhaust mixture before the air and exhaustmixture enters power source 10. With reference to FIGS. 2 and 3, the airand exhaust mixture may enter inlet 66 of first body 56 and be conductedthrough first body 56 to inlet 71 of second body 58. After enteringinlet 71 of second body 58, the air and exhaust mixture may pass throughthroat section 74, where the pressure of the mixture may decrease andthe velocity of the mixture may increase relative to the pressure andthe velocity of the air and exhaust gas mixture at an upstream location(e.g., at inlet 66 of first body 56). Thus, throat section 74 may createa pressure differential between the accelerated fluid internal to throatsection 74 and the unaccelerated fluid external to throat section 74(e.g., the fluid located in annular reservoir 62).

As the air and exhaust mixture passes through condensation reductiondevice 27, condensate flowing along internal surface 80 of first body 56may collect in annular reservoir 62. Heater 64 may transfer thermalenergy into the condensate in annular reservoir 62. The thermal energymay convert some of the liquid condensate into a gaseous phase and mayfurther promote atomization of the condensate at throat section 74.

The gasses and atomized condensate may then be drawn from annularreservoir 62, through passageway 60 via the pressure differential atthroat 74, and propelled or injected into the accelerated stream of airand exhaust. Introduction of the condensate into the accelerated flow atthroat section 74 may, via changes in the pressure, temperature,velocity, and surface area of each condensate fluid particle,re-entrain, and revolatilize the condensate into the air and exhaustmixture. The mixture of air, exhaust, and re-entrained condensate maythen pass through fluid passageway 33 to intake manifold 25 forsubsequent combustion within power source 10.

Several advantages of the disclosed fluid handling system may berealized. In particular, the disclosed condensation reduction device mayatomize and re-entrain liquid condensate into the flow of air andexhaust prior to entering the associated power source. The redispersionof the condensate may help prevent wear of the power source andcorrosion within the disclosed air induction system downstream of thecondensation reduction device. Furthermore, the disclosed fluid handlingsystem may improve the emission characteristics of the power source byredispersing the condensate into the flow of air and exhaust rather thanremoving it.

It will be apparent to those skilled in the art that variousmodifications and variations can be made to the disclosed fluid handlingsystem. Other embodiments will be apparent to those skilled in the artfrom consideration of the specification and practice of the disclosedfluid handling system. For example, the disclosed condensation reductiondevice could alternatively or additionally be located just downstream ofthe exhaust cooler to re-entrain exhaust condensate prior to mixing withair, if desired. It is intended that the specification and examples beconsidered as exemplary only, with a true scope being indicated by thefollowing claims and their equivalents.

1. A condensation reduction device, comprising: a first body positionedto receive a flow of exhaust from a power source; a reservoir in fluidcommunication with the first body configured to collect condensate fromat least the flow of exhaust; and a passageway in fluid communicationwith the reservoir configured to direct the collected condensate fromthe reservoir back into at least a portion of the flow of exhaust priorto the at least a portion of flow of exhaust entering the power source.2. The condensation reduction device of claim 1, wherein the at least aportion of the flow of exhaust is first combined with air before beingreceived by the first body.
 3. The condensation reduction device ofclaim 2, further including a second body located downstream of the firstbody, wherein the second body includes an inlet portion extending intothe first body, and the inlet portion of the second body has an outersurface spaced apart from an inner surface of the first body to form thereservoir.
 4. The condensation reduction device of claim 3, furtherincluding a sealing member disposed between the first body and thesecond body to restrict the flow of fluid from the reservoir.
 5. Thecondensation reduction device of claim 3, wherein the first body and thesecond body are integral.
 6. The condensation reduction device of claim3, further including a constriction in an inner diameter of the secondbody configured to draw condensate from the reservoir into the flow ofair and exhaust.
 7. The condensation reduction device of claim 6,wherein the passageway extends into the flow of air and exhaust suchthat the condensate is directed into a center portion of the flow of airand exhaust.
 8. The condensation reduction device of claim 6, wherein aninlet of the passageway is located at a gravitationally lower portion ofthe reservoir.
 9. The condensation reduction device of claim 6, furtherincluding an expanded section located downstream of the constriction,wherein an angle of expansion at the expanded section is approximately 6degrees.
 10. The condensation reduction device of claim 1, wherein thefirst and second bodies are tubular.
 11. The condensation reductiondevice of claim 1, further including a heater associated with thereservoir to promote atomization of the collected condensate.
 12. Thecondensation reduction device of claim 11, wherein the heater isconfigured to receive a fluid.
 13. The condensation reduction device ofclaim 1, wherein the reservoir is annular.
 14. A method of re-dispersingcondensate, comprising: generating a flow of exhaust; mixing the flow ofexhaust with air; cooling the mixed flow of air and exhaust; collectingcondensate from the cooled and mixed flow of air and exhaust; anddirecting the collected condensate back into the cooled and mixed flowof air and exhaust prior to combustion of the cooled and mixed flow ofair and exhaust.
 15. The method of claim 14, wherein directing includesdrawing the collected condensate from an outer periphery of the cooledand mixed flow of air and exhaust toward a center of the cooled andmixed flow of air and exhaust.
 16. The method of claim 15, whereindrawing includes creating a pressure differential between the collectedcondensate and the cooled and mixed flow of air and exhaust.
 17. Themethod of claim 14, further including heating the collected condensateto promote atomization of the collected condensate.
 18. The method ofclaim 14, wherein: collecting includes directing the condensate radiallyoutward and blocking the condensate from flowing in the direction of themixed and cooled flow of air and exhaust; and directing includesdirecting the condensate radially inward to the cooled and mixed flow ofair and exhaust.
 19. A fluid handling system, comprising: a combustionengine configured to produce a mechanical power output and a flow ofexhaust; an exhaust passageway fluidly coupled to direct exhaust fromthe combustion engine to the atmosphere; an induction passagewayconfigured to direct air to the combustion engine; a recirculationpassageway configured to direct exhaust from the exhaust passageway intothe induction passageway; a cooler disposed in fluid communication withthe induction passageway to cool air and exhaust directed to the engine;and a condensation reduction device having: a first body configured toreceive the cooled air and exhaust; a reservoir in fluid communicationwith the first body to collect condensate from cooled air and exhaust;and a passageway in fluid communication with the reservoir to redirectthe collected condensate into the flow of cooled air and exhaust. 20.The fluid handling system of claim 19, further including a constrictionin an inner diameter of the second body configured to draw condensatefrom the reservoir into the flow of air and exhaust.